Cambering mechanism for grinding machines



Aug. 26, 1941. c. L. scHULTE ET AL CAMBERING 'MECHANISM FOR GRINDINGMACHINES 4 Sheets-Sheet l Filed Nov. '7, 1958 ATTORNEY.

Aug 26, l941- c. L. scHuLTE ETAL 2,254,020

` CAMBERING MECHANISM FOR GRINDING MACHINES Filed Nov. 7, 19:58 4sheets-sheet 2 ATTORNEY.

Aug; 26, i941. c. 1 scHULTE ET AL 2,254,020

CAMBERING MEGHANISM FOR GRINDING MACHINES Filed Nov. `7, 1958 4sheets-sheet 3 ATTORNEY.

Patented Aug. 26, 1941 CAMBERING MECHANISM FOR GRINDING MACHINESClifford L. Schulte, Rossmoyne, and Andrew J. Graf, Norwood, Ohio,lassignorsto Cincinnati Grinders Incorporated, Cincinnati, Ohio, acorporation of Ohio Application November 7, 1938, Serial No. 239,294

11 Claims.

This invention relates to grinding machines and more particularly to thetype of machine utilized for producing cambered surfaces on work. Y

One ofthe objects of this invention is to produce a camber grindingmachine which has a sufliciently large range of adjustment to encompassall commercial cambers now being produced.

Another object of this invention is to provide a cambering mechanism fora grinding machine which is rugged in construction and which, althoughadjustable, has all of the adjustable parts positively connected andpositively driven.

A further object of this invention is to provide a cambering mechanismwhich is simple in construction, which may be positively set, and whichmay be reset in exactly the samel condition to reproduce a given camber.

Other objects and advantages of the present invention should be readilyapparent byV reference 20 to the following specification, considered inconjunction with the accompanying drawings forming a part thereof and itis to be understood that any modications may be made in the exactstructural details there shown and described,

within the scope of the appended claims, without departing from orexceeding the spirit of the invention.

Referring to the drawings in which like reference numerals indicate likeor similar parts:

Figure 1 is a cross sectional view through a grinding machine embodyingthe principles of this invention.

Figure 2 is an enlarged view of the camber vcontrol mechanism as viewedon the line 2-2 of Figure l. Y Y

Figure 3 is an expanded view of the cambering mechanism showing thedrive arrangement as viewed on the line 3-3 of Figure 2.

Figure 4 is a plan View showing camber control parts locked together fordriving.

Figure 5 is a view similar to Figure 4 with the parts unlocked and inposition for adjustment.

Figure 6 is a section on the line 6 6 of Figure 4.

Figure '7 is a diagrammatic view showing the relative relation betweenthe grinding wheel and work during adjustment of the camberingmechanism.

Figure 8 is a detail view showing the table driving mechanism.

Vsupporting a work piece, which is indicated in the rawings bythereference numeral I4. The work is rotated relative to the rotatablegrinding wheel I5, and is also adapted to be traversed axially relativeto the wheel when it is longer than the face of the grinding wheel iswide. This traversingmovement may be effected by power means, such asthat shown in Figure 8, and consisting of a power operated motor I6which rotates a worm I1 through drive shaft I8. The worm intermesheswith a worm gear I9 secured to the end of shaftrZIl which also haspinion 2| intermeshing with a rack 22 .secured to theunderside of thetable.

For producing cambered work, such as rolls for steel millsrand the like,it is necessary to produce a second relative movement between thegrinding wheel and the work and in a direction at right angles to thedirection of traverse so that the diameter of the work may be graduallyyincreased or decreased in a uniform .manner during traverse. By propercontrol of this movement, various cambers of either a lconvex or concavevariety vmay be produced.

The mechanism for producing the cambering movement ofthe wheel ispositively driven in timed relation with the traverse of the table andis adjustable tovproduce any commercial camber now in use. The mechanismfor setting and locking the adjustable parts for a given camber is soaccurate that it may be reset in exactly the same position to reproducea given scamber.

TheV cambering mechanism receives its power from the movingftable so asto be in timed relation therewith, and as shown, the table rack 22rotates a pinion 23 and its supporting shaft 24, the latter beingjournaled in the bed. This shaft carries a bevel pinion 25 fortransmitting rotation to-,a bevel gear 26 secured toa sleeve 21. Thesleeve is supported for rotation in the bed and has a splined bore 28 bywhich it is operatively connected tothe splined end 29 for rotation ofshaft 30. The shaft 30vextends to the rear of the machine where it isprovided with ay pinionY 3| for rotating a pair of change gears 32 and33 through pinion 34 and shaft 35. The gear 33vis keyed to the end ofshaft 33 which has a gear 31 keyed to the other end and meshing withspur gear 38. It will be noted that the'gears 34, 32 and 3Iare allpositively keyedv to their respective shafts.

The gear 38 is supported for axial movement relative to a supportingsleeve 39. ,When the gear 38 is in driving position, internal teeth 40on the gear intermesh with external teeth 4I formed on the end of thesleeve 39 and this forms Ia positive driving connection between the gear38 and the sleeve 39. 'I'he gear 38 is capable of suicient 'axialmovement tol disengage teeth 40 from teeth 4I while remaining in meshwith thel gear 31.V When this driving connection is broken `the sleeve39 is free to be rotatably adjusted while the gear 38 is held againstrotation by the gear 31. The sleeve 39 is anti-frictionally suported forrotation on a fixed stud 42 and the teeth 4I are concentric with respectto the axis of the stud. The sleeve, however, has an eccentric portion43 upon which is supported a cam member 44 having a cam track 45 whichis eccentric with respect to the axis of its bore 4E. The eccentricityof the periphery of the sleeve with respect to the axis of the stud 42is equal to the eccentricity of the periphery of the cam track withrespect to its bore, whereby if these two parts are relatively adjustedso that the eccentricities are opposite to one another, the center ofthe cam track 45 will lie in the axis of the stud 42 and no resultanteccentricity, so far as the cam track is concerned, will be present.With the parts in this position the eccentricity may be said to be zero.

The grinding wheel I5 is supported for rotation on a longitudinallymovable slide 41 which also carries the prime mover, such as 48, forrotating the grinding wheel. 'Ihe slide 4l may be traversed by anyconventional form of mechanism, but since this mechanism forms no partof the present invention the same is not illustrated herein. The slide41 is guided on a support 49 which is adapted to be oscillated relativeto the bed l to effect movement of the grinding wheel in a substantiallyradial direction with respect to the work. To this end a pivotedconnection 50 is provided and it will be noted that the axis of thispivot is directly below the grinding wheel. The free end of support 49rests on a plunger I which has a roller 52 riding on a lever 53 as shownin Figure 2. The lever 53 is fulcrumedv at 54 in the bed of the machineand the free end of the lever is provided with a fcllower roller 55which engages the periphery of the cam track 45. It should new beapparent that if the axis of rotation of the cam is concentric with the'axis of the stud 42, no oscillation of the lever 53 will take place,and therefore, a true cylindrical surface will be produced on the work.

It is common practice in setting up for a given camber to iirst positionthe table longitudinally to place the longitudinal center of the workop- '.Oosite the center of the grinding wheel face. In other words, theparts will be in the position diagrammatically indicated: in Figure 7.The cambering mechanism is then adjusted to the desired setting. Itwill, therefore, be assumed that the work and grinding wheel are in therel.- ative positions indicated in Figure '7 while making the followingadjustments.

Referring to Figures 9, and l1. the carn track 45 and the eccentricsleeve portion 43 'are illustrated diagrammatioally to show therelationship of the eccentrics. The reference numeral 56 indicates thecenter of the fixed stud 42 which is also the center of rotation of theparts during operation of the machine. The periphery of the eccentricsleeve portion 45 is a true circle 'and its geometrical center isindicated by the numeral 51. In the position of zero camber the center51 lies on 'axis 53-58 which is perpendicular to the axis 59--59 passingthrough the center of rotation 5S and the center of the follower roller55.

The periphery of the cam track 45 is also a f true circle, the geometriccenter 60 of which is superimposed on the center 56 in the zero camberposition indicated in Figure 9. Therefore, since the geometrical centerof the cam track lies in the center of rotation it is apparent that theparts can be jointly rotated without effecting movement of the grindingwheel either toward or from the work.

As shown in Figures 4 and 5, the cam member 44 and the sleeve 43 areprovided with Zero graduation marks 6I and 62 respectively. When theparts are in the position shown in Figure 9, the Zero marks 6| and 52are in alignment with a third zero mark 63 formed on the periphery of aplate 54 permanently attached to the end of the stud 42. This plateserves to retain thc sleeve on the stud. Thus, when vall three zerograduation marks are aligned, it automatically places the parts in zerocamber position.

It will be evident that in initially moving the grinding wheel toward oraway from the work that the center of the cam track 45 must when shiftedremain on the axis 59-59 if the maxlmum or minimum setting is to beobtained, the direction of shifting depending upon whether the camber isto be concave or convex. It will be evident that with the center 6!)above or below the center of rotation 56 that the cam track will producethe same eiect as regards the amount 'and direction of movement of thegrinding wheel with respect to the work regardless of its direction ofrotation.

The shifting of the center of the cam track above lor below center isaccomplished in part by rotating the sleeve 39 and in so doing the axis58-58 will rotate about the center 55 into some assumed position, suchas that shown in Figure 10. Assuming the cam held against rotation, theaxis 65-65 which connected the centers 5'! and 60 will move laterallydownward to the position shown in Figure 10 and since the geometricalcenter of the cam track lies on this axis and is a fixed distance fromthe center 5?, the center 5D must have shifted not only downward but tothe right of 'axis 59--59.

It is necessary, however, as stated supra, that the center 65 lie on theaxis 59. This may be accomplished by rotating the axis about the center51 through an angle equal to the angle through which the axis 58 wasrotated about the center 56.

When this is done the parts will be in the position shovm in Figure 1land the angle 66 will be equal to the angle 5l. This will reposition thecenter 55 of the cam track on the axis 59, but a desired amount above orbelow center to produce the desired camber at the center of the work. Itwill be noted that the axis 58 was rotated in a counterclockwisedirection while the axis was rotated in a clockwise direction. That isthe reason why the graduations on the sleeve and cam extend in oppositedirections from the respective Zero points in Figures 4 and 5. Theindividual rhombs of the scale may be numbered consecutively, and aseparate chart provided to show the amount of camber for differentposition combinations. It will be evident that the angle of rotation ofthe cam and sleeve must be equal and opposite in order to have'thecenter of the cam track lie on the perpendicular axis passing throughthe center of a follower roller so that the rate of increase or decreasein the camber will be the saine for either direction of rotation of thecam track. Therefore, the sleeve and cam are rotated until the samegraduation numbers are aligned with the zero mark 63 on the plate 54. Itis then only necessary to shift the cam member 44 axially to effectengagement of teeth 45 and 4|. The cam member must now be secured to thesleeve for rotation therewith and this is accomplished by providing aseries of equally spaced radial graduation holes 68 in the sleeve 39 andall lying in a single plane.l In addition, the cam member is providedwith a series of equally spaced radial Vernier holesr 69, but spacedcloser than the holes in the sleeve. f

These holes are so spaced that for each setting only one pair of holeswill be in alignment. A locking pin is inserted in the aligned holes andif the holes are slightly out of alignment, the insertion of the pinwill automatically correct the alignment. This makes it possible torepeat a setting with absolute accuracy and without depending upon theability of a workman to align exactly two graduation marks. The pin alsoserves as a positive driving connection between thejsleeve and the cammember. The locking pin has an annular groove ,'H formed therein forengagement with a spring pressed -detent 72, as more particularly shownin Figure 3. This prevents the pin from accidentally becoming removedduring rotation of the parts.

The following method is utilized for changing Athe set-up of thecambering mechanism.- The rear end of the grinding wheelsupport 49 iselevated to take the weight 01T of the cam member. For this purpose alifting bolt 1,3 having a hexagonal head 'I4 fitting into a hexagonalsocket 15 in the end of lever 53 is passed through the frame 'IGVandprovided with a nut 17 whereby rotation of the nut will effect axialmovement of the bolt T3. A commercial form of ratchet wrench 'I8' isprovided for rotating the nut 11.

, When the weight of the grinding wheel support has been removed fromthe cam, the driving pin 1U is removed and the cam member 44 is pulledoutward, disengaging the kteeth 4| from the teeth 40 on the sleeve 39.The sleeve and camare now `free to be rotated. The same number on eachscale of the cam and sleeve are now broughtinto vregister with the xedzero mark 63 on the mem..

lber 54. This operation properly positionsY the eccentrics relative toone another and itis only necessary to lock them in this position. Thisis accomplished by moving the cam member laxially which effectsre-engagement of the teeth 40 and 4l, thereby connecting the sleevepositively to itsactuator 38, and reinserting the driving pin 'l0 whichpositively connects the cam to the sleeve for joint rotation-therewith.Attention is invited ytol the fact `that the teeth 4B vand 4I are madevsufficiently small so that no rotationl of the sleeve is necessary toeffect interengagement of the teeth for any given setting thereof.

. -Since the cam is driven by the table itl is Anejoessary that the camrotate'in absolute'synchro.- nism with table movement, and means aretherefore provided for removing all backlash in the drive from the tableto the cam, and in such a way that the gear teeth always contact non thesame side. This is accomplished by providing a hydraulic motor 19, asshown in Figure 3 :and connecting the gear 8l) of the motor through apair of integral gears 8| and 82 to the gear 38.

By establishing a predetermined pressure in the hydraulic motor T9 aresistance maybe created by the motor which must be overcome by thetable drive motor I6, thereby taking out all the backlash when drivingin one direction. In order to maintain the gear tooth contact as createdby this condition, the motor I9 is made to serve as the dominant motorduring travel in the other direction by increasing the pressure inthemotor above that in motor I6.

Y l There has thus been provided an improved form of cambering mechanismwhich may be more accurately set up than previous devices, and in whichall the parts are positively driven, thus insuring asafer mechanism andone which may be very accurately reset for renishing ground cambersurfaces.

What is claimed is:

1. In a roll grinding machine having a power translatable work table anda pivoted grinding wheel support for moving a grinding wheel carriedthereby toward and from the work table, the combination of means fortilting said support including a rotatable cam, a fixed stud, a sleevehaving a portion eccentrcwith respect to the stud, for supporting thecam on the stud, a gear train driven by the table and including a nalgear, concentric with the stud,l means for acljustably interconnectingthesleeve with said gear for rotation thereby, means to connect the camto 4the sleeve, said last-named means being removable to permit axialshifting-of the cam member -relative to thesleeve, and means 'operableby `shifting of the cam, member for disconnecting grinding wheelsupport, the combination of means for tiltingsaid support includng aiixedstud, a

eeveV eccentricallyfmounted on the stud, a cir- 'cular cam eccentricallymounted on the sleeve, means to secure the cam andsleeve together indilferent relativerotated positions yielding different eccentrcities ofthe cam with respect to the center of the stud including a series ofgraduation holes inone member, a series of Vernier holes in the othermember, a driving pin insertable in aligned holes,` and power operablemeans positively connectible for rotating the sleeve.

3. In a roll grinding machine having a tiltable Ygrinding wheel support,the combination of means for tilting said support including a iixedstud, a sleeve eccentrically mounted on the stud, a circular cameccentrically mounted on the sleeve, means to secure the cam and sleevetogether in different relative rotated positions yieldingdifferent'eccentricities of the cam with respect to the center of thestud including a series of graduation `holes in onemember, a series orVernier holes in the other member, a driving pin insertable in thealigned holes,vpower operable means positively connectible for Vrotatingthe sleeve, and means to the center of the stud including a series ofgraduation holes in one member, a series of vernier holes in the othermember, a driving pin insertable in aligned holes, detent means forholding the driving pin in driving relation and power operable means forrotating the sleeve.

5. In a roll grinding machine having a supporting frame and a grindingwheel support pivotally connected at one end to the frame, thecombination of means for tilting said support including a xed stud, asleeve eccentrically mounted in the stud, a circular cam eccentricallymounted on the sleeve, a lever pivotallyr connected at one end to theframe and having the other end resting on the cam, said support restingon the lever midway of the length thereof, said cam and sleeve beingrelatively rotatable to yield diierent eccentricities of the cam, andmeans for actuating said lever to remove the weight of the support onthe cam during said adjustment,

6. In a machine of the character described, means for eiecting acontrolled variable oscillation of a grinding wheel support, including asupporting stud, a drive train including a sleeve rotatably butnon-translatably mounted on the stud, Said sleeve having a concentricand an eccentric bearing portion, a drive train including a drive gearrotatably and translatably mounted on the concentric portion of thesleeve, a cam member rotatably and translatably mounted on the eccentricportion of the sleeve, interengageable means on the gear and sleeveeiective in one position of relative translation of the parts to lockthe gear and sleeve against relative rotation, and connections betweenthe cam member and gear for effecting said interlocking engagement.

7. In a machine of the character described, means for eiecting acontrolled variable oscillation of a grinding wheel support, including asupporting stud, a drive trainincluding a sleeve rotatably butnon-translatably mounted on the stud, said sleeve having a concentricand an eccentric bearing portion, a drive train including a drive gearrotatably and translatably mounted on the concentric portion of thesleeve, a cam member rotatably and translatably mounted on the eccentricportion of the sleeve, interengagable means on the gear and sleeveeffective in one position of relative translation of the parts to lockthe gear and sleeve against relative rotation, connections between thecam member and gear for effecting said interlocking engagement, andmeans for locking the parts in engaged position. Y i

8. In a machine of the character described, a wheel head oscillationcontrolling mechanism including a fixed stud, a sleeve rotatably mountedon the stud having a concentric and an eccentric bearing portion, adrive gear rotatably mounted on the concentric portion and anoscillation cam member rotatably mounted on the eccentric portion of thesleeve, means securing the sleeve for rotation on but against axialmovement with respect to the stud, means rotatably coupling the cammember and gear elements for relative rotary and joint reciprocatingmovements, a multiple interlocking device carried by the gear and sleeveadapted for interengagement on translation of the gear in one directionto secure the gear and sleeve for joint rotation at any selectedrelative angular adjustment thereof, and additional means for securingthe cam in rotatively adjusted position with respect to the sleeve.

9.1n a machinerof the character described, a Wheel head oscillationcontrolling mechanism including a xed stud, a sleeve rotatably mountedon the stud having a pair of exterior bearing portions, one of which isconcentric with the stud and the other eccentrically disposed withrespect thereto, a driving train including a gear rotatably mounted onthe concentric portion of the sleeve and formed with a shifting spool, acam member rotatably mounted on the eccentric bearing portion having ashifter interengaged with the spool of the gear, a rst means retainingthe cam member on the sleeve for limited axial movement with respectthereto whereby the cam may be translated to effect limited shifting ofthe gear axially with respect to the sleeve, and interengaging clutchmeans on the sleeve and gear in one direction for effecting drivingengagement between the gear and sleeve.

10. In a machine of the character described, a wheel head oscillationcontrolling mechanism including` a fixed stud, a sleeve rotatablymounted on the stud having a pair of exterior bearing portions, one ofwhich is concentric with the stud and the other eccentrically disposedwith respect thereto, a driving train including a gear rotatably mountedon the concentric portion of the sleeve and formed with a shiftingspool, a cam member rotatably mounted on the eccentric bearing portionhaving a shifter interengaged with the spool of the gear, a first meansretaining the cam member on the sleeve for limited axial movement withrespect thereto whereby the cam may be translated to effect limitedshifting of the gear axially with respect to the sleeve, interengagingclutch means on the sleeve and gear in one direction for effectingdriving engagement between the gear and sleeve, and means for securingthe cam member and gear against movement with respect to the sleeve.

11. In a machine of the character described, a wheel head oscillationcontrolling mechanism including a fixed stud, a sleeve rotatably mountedon the stud having a pair of exterior bearing portions, one of which isconcentric with the stud and the other eccentrically disposed withrespect thereto, a driving train including a gear rotatably mounted onthe concentric portion of the sleeve and formed with a shifting spool, acam member rotatably mounted on the eccentric bearing portion having ashifter interengaged with the spood of the gear, a rst means retainingthe cam memberv on the sleeve for limited axial movement with respectthereto whereby the cam may be translated to effect limited shifting ofthe gear axially with respect to the sleeve, interengaging clutch meanson the sleeve and gear in one direction for effecting driving engagementbetween the gear and sleeve, the sleeve having a series ofcircumferentially arranged sockets formed therein, and a locking devicecarried by the cam member and selectively engageable in the sockets ofthe sleeve when said member is axially positioned to effectinterclutching engagement between the gear and sleeve, whereby saidmember simultaneously secures the gear and sleeve against axialdisengaging movement and the member and sleeve against relative rotarymovement.

CLIFFORD L. SCI-IULTE. ANDREW J. GRAF.

